Method and apparatus for controlling flow of fluids



April 29, 1941.

N. BORRESEN 2,240,436

METHOD AND APPARATUS FOR CONTROLLING FLOW OF FLUIDS Filed April 9, 1938 3 Sheets-Sheet 1 INVENTOR ATTORNEYS APrilv29, 1941- N. BoRREsEN 2,240,436

METHOD AND APPARATUS FOR CONTROLLING FLbW OF FLUIDS Filed April 9, 193a 3 Sheets-Sheet 2 1N VENTOR Nico Bormsen, @mw, M,

A TORNEYS April 29, 1941. N. BORRESEN 2,240,436

METHOD AND APPARATUS FOR CONTROLLING FLOW OF FLUIDS Filed April 9, 1938 3 Sheets-Sheet 3 ATTO-RN EYS Patented A r. 29, 194i UNITED res PATENT "FFICE Marnop AND APPARATUS FDR oon'monnrne now or ramps Nico Bor-resen, Buffalo, N. Y2, assignor to Nicostat Products 00., Buflalo, N. Y.

Application April 9, 1938, Serial No. 201,118

15 Claims. I (Cl. 137-139) Another object of the invention is to providean improved method and means for introducing a fluid fuel into the combustion chamber of a fuel burning apparatus at a varying rate and in accord with the fuel-consuming ability of the burning apparatus under different operating conditions.

Another object of the invention is to provide an improved method of introducing fluid fuel into the combustion chamber of an intermittently op.- erated fuel burning apparatus including the provision of an initial fluid flow at a restricted rate during the early stages of each combustion operation and a full normal operating rate of flow subsequent to a predetermined time lapse.

of the valve element in response to such fluid pressure differential forces thereof are automatically restricted in rate of motion in varying degrees.

Another object of the invention is to provide an improved valve motion restricting mechanism embodying a control member adapted to change in form in response to changes in the temperature thereof and a controlled electrically resistant conductor associated therewith for effectin changes in the temperature thereof, and means Another object of the invention is to provide an improved method and means for automatically varying the rate of fuel flow into the combustion chamber of a burning apparatus in such manner that during the initial stages of combustion operation the rate of fuel flow is restricted in a predetermined manner until such time as temperature and draft conditions in the burning apparatus assume substantially normal operating conditions, at which time a full flow .of fuel at the normal operating rate is permitted.

Another object of the invention is to provide an improved fluid control valve mechanism for the purpose described and in which resistance to fluid'flow therethrough during normal full-flow operating conditions is at a minimum.

"-Another object of the invention is to provide an improved fluid control valve mechanism which is automatically operable in response to a control therefor to provide a slowly increasing rate of fluid flow therethrough for a predetermined time during the valve opening process until full flow conditions are attained.

Another object of theinvention is to. provide an improved fluid control valve mechanism wherein the main valve element is adapted to be actuated toward open and closed positions by fluid pressure difierential conditions operating upon the valve element, and in which movements for effectively ventilating the elements of the mechanism so as to provide for quick response of the control element to temperature adjustments.

Other objects and advantages will appear in the claims and in the specification herein which is exemplary of the invention.

In the drawings:

Fig. 1 is a diagrammatic illustration of a fluid fuel burning apparatus employing a valve control mechanism of the invention;

Fig. 2 is a graphic illustration of movement of the main valve element of the fluid control mechanism during one complete hypothetical cycle of fuel burning operation;

Fig. 3 is a section through a valve mechanism embodying the principles of the invention;

Figs. 4 and 5, are views, on enlarged scales, of

portions of the valve movement restricting mechanism of Fig. 3;

Fig. 6 is a view, similar to Fig. 5 of another form of construction of the valve movement restricting mechanism;

Fig. 7 is a transverse section on an enlarged scale through a portion of the mechanism of Fig. 3; and

Figs. 8 to 12 are diagrammatic views of portions of the fluid flow control mechanism of Fig. 3, showing the parts in diflerent operative positions.

Referring to the drawings, the invention is shown as being supplied in connection with a fluid control valve structure that is particularly efrective in connection with the control of fluids such as gaseous or liquid fuels in connection Fig. 1 illustrates supplied with a gaseous or liquid fuel through means of a conduit 12, the flow of which is controlled by a valve mechanism H of my novel construction. The valve mechanism I4 is adapted to be controlled automatically by means of a thermostat device l6 which is connected in. series with a source l8 of electric current and the valve actuating mechanism of the device.

The valve actuating mechanism of the device is adapted to provide for an initial opening of reduced size through'the valve device in response to valve opening control movements of the thermostat l8, and a gradual increasing of, the size of the opening through the valve device during an adjustable predetermined lapse of time prior to attainment by the valve of a completely opened position for full operating flow therethrough. Also, in response to valve closing movements vof the thermostat device iii, the valve control mechanism is initially actuated to a reduced fluid flow position and then subsequently gradually actuated toward increasingly reduced 'flow positions until a completely closed valve position is at-' tained. Hence, means are-provided for introducing a reduced flow of fuel into the combustion chamber of a fuel burning apparatus during the early stages of combustion operation, and subsequently increasing the flow of fuel as temperature and draft conditions within the combustion chamber become such as to enable the device to accommodate increasingly greater rates of fuel flow, until full operating conditions are attained. Hence, the possibility of flare-backs due to overloading the combustion chamber prior to the attainment of normal operating conditions therein is avoided, along with the danger and noise that is otherwise attendant thereto. Also, in connection with the termination of the fuel burning process, the cessation of fuel flow is I accomplished in a gradual manner, and hence the possibility of producin concussions in the fuel supply system is obviated, and the danger of accidentally extinguishing or disturbing the pilot light by such action is precluded. The fluid con-- trol features described generally hereinabove are: adjustable for functioning in varying marine s so that a wide'range of variable performance c acteristics may be obtained.

As illustrated more particularly in Fig: 3, the control valve mechanism herein includes a valve casing 38 provided with an inlet port 82, an outlet port 34, and an inner partition wall 86. An upper wall portion of the partition memberis: formed with a circular opening 38 into which is tightly fitted an upwardly extending cylindrical collar 40, the upper marginal edge portion of which is adapted to constitute an annular valve seat for the primary valve of the mechanism to be hereinafter described. Immediately adjacent and above the valve seat member 40 and in open communication with the inlet part 32 is provided a circular valve chamber 42 disposed in concentric. relation with the valve seat member 48. The

valve chamber 42 is of a diameter substantially greater than that of the annular valve seat member 40 and is, adapted to freely accommodate therein a primary valve member 44 of disc form the device. The primary valve 44 is of a diameter slightly less than that of the valve chamber 42 so that a' small annular-shaped gap 48 is provided between the marginal edge of the valve and the wall of the casing in the region of the chamber 42.

An auxiliary valve chamber 48 is provided in the upper interior portion of the casing 88 in open communication with the valve chamber 42 and is provided with an auxiliary outlet port 49 leading to the main outlet port 3401 the casing,

An auxiliary valve 58 for closing the auxiliary outlet port 49 is mounted in free-swivelling relation upon one end of a lever arm 52 by means of cooperation between a bifurcated finger piece 54 extending in spaced relation therefrom and an enlarged boss 56 formed integral with the auxiliary valve 58. The lever 52 is fulcrumed for pivotal action within the chamber 48 upon a downwardly extending portion of a bracket 58 which is rigidly mounted upon the casing structure. A'

coil spring 88 is arranged in such manner that one of its ends bears against the lever 52 at an end portion opposite to the auxiliary valve carrying end thereof and at a position spaced from the point of pivoting upon the'bracket 58. The other end of the coil spring 68 bears against a shoulder piece 82 extending rigidly from a portion of the casing.

An electro-magnetic device comprising a coil 85, a core, and opposed pole pieces 61 and 68 is mounted upon the upper portion of the valve casing 38, with the ends of the poles Hand 68 extending through suitable openings in the upper wall of the casing and their terminals disposed adjacent opposite ends of the lever 52-. Suitable binding posts 18 are connected to opposite ends of the coil 85 for detachable connection thereto of conductors 12 arranged to provide a circuit .in series --with the source- I 8 of electric current and the control-device l8. When the circuit is closed by operation of the device IS the flow of current through the circuit energizes the coil 65 so that the lever is pivotally moved about the arm 58 in such manner that the auxiliary valve 58 is moved away from valve seat contacting position against the action of the spring 80. Whenever the electro-magnet actuating circuit is open, as by reverse operation of the device IS, the magnetic action of the poles 61 and 68 is terminated and the spring 68 causes the lever to return toward a position wherein the auxiliary valve 58 closes the auxiliary outlet port 49. r

A valve movement restricting mechanism for the primary'valve 44 is shown herein as comprising essentially a cantilever spring arm 88 formed of bi-metal in accord with conventional thermostatic practice so as to be adapted to bend in the presence of changing temperature conditions. The arm is fixedly mounted at one of its ends to a stationary portion of the valve casing structure, as by means of a threaded pin and nut unit 82 (Fig. 4). The other end of the arm is connected to the main valve 44 through means of an intermediate adjustment leaf 84 and a swivel pin 88. The pin 86 is enlarged atits lower end and is provided intermedially thereof with a reduced section 88 (see Fig. 5) to provide for a swivel connection with ,opposed portions of a bifurcated clamp 98 which extends rigidly from the main valve. The upper terminal portion of the pin enlargement is formed to provide a rounded shoulder 92 for bearing against the un- 'portion adapted to provide a swivelling fit between the leaf 84 and the rounded shoulder 92 of the pin.

An adjustment screw I is carried by the free end of the cantilever arm 80 in screwthreaded relation therewith (Fig. 7) and is arranged to have one end extending therefrom to bear against an intermediate portion of the leaf 84 to provide means for adjusting the attitude of the valve carrying end of the leaf 84 relative to the bimetal arm B0.

An element for heating the bi-metal arm 80 is shown as comprising an electrically resistant conductor I in the form of a wire wound about the bowed or intermediate portion of the bi-metal arm 80 and having its opposite ends connected to binding posts I I0 from which a pair of conductors I05 (Fig. 1) are arranged to lead to pointsof connection with the conductors I2 of the electromagnetic control circuit. A switch I0I is preferably arranged in the line of one of the conductors I06 to provide for optional discontinuance of the operation of the heating element I05 independently of the control of the electromagnetic operating circuit. The heating element I05 iselectrically insulated in some suitable manner to prevent its being grounded upon the bi-metal arm 80, and such insulation is preferably provided of minimum thickness and heat insulating capacity so that the heat generated by transmission of electric current from the source I8 through the element I05 will be quickly andefficiently conveyed to the adjacent portion of the bi-metal arm 80.

When installed in the line of a fluid carrying conduit, as illustrated in Fig, 1, the valve device is adapted to control the flow of fluid therethrough in a novel and advantageous manner in connection with a variety of applications. For example, application of the device to the control of fluid fuel flow into a. heater apparatus, as

valve 50 is seated in a closed position relative to the conduit 49, thus providing a built-up static fluid pressure within the valve chambers of the device above the main valve 44 by reason of which this valve is held firmly in a closed position against its valve seat 40, and flow of fluid through the conduit I2 is'prevented. The operation of the static fluid pressure upon the upper surface of the valve 44 is produced by reason of the free passage of fluid from the inlet port side of the partition 36 through the gap 46 between the valve 44 and the adjacent wall portion of the valve chamber 42 and into the valve chambers above the main valve 44. Whenever the auxiliary valve 50 is closed the static fluid pressure of the line thus tends to maintain the main valve firmly seated in the closed position.

Whenever the control device I6 becomes adjusted to a circuit closing condition, as for example, in response to a reduction in the temperature of the atmosphere of the room adjacent thereto below a. predetermined limit, 01' actuation of some time-controlled element, the electro-magnetic control circuit of the conductors I2 will be closed and the electro-magnetic device of the mechanism will be caused to actuate the lever 52 as described hereinabove to raise the auxiliary-valve 50 to an open position relative to the auxiliary conduit 49. When the auxiliary outlet port is thus opened the static fluid pressure above the main valve 44 is relieved by escape of fluid from the valve chambers through the outlet ports of the mechanism, and the primary valve 44 becomes subjected to a differential of fluid pressure forces 'which is in favor of the forces tending to lift the valve away from its valve seat. The valve lifting forces referred to comprise dynamic fluid pressure forces due to flow of fluid from the inlet port and along side the marginal edges of the primary valve through the gap 46' toward the outlet port and an unbalanced static fluid pressure force representing the difference between the static pressure of the line below the valve in the inlet end of the line and the static fluid pressure in the outlet end of the line. The composition of these valve lifting forces are more than suflicient to overcome the weight of the valve 44 and tend to lift it bodily within the valve chamber 42 away from the valve seat 40, and if left unrestrained would immediately move the valve 44 to its wide open position thus permitting a full normal operating flow of fluid through the mechanism immediately upon actuation of the control device I6 to oper ative position.

In the case of fluid fuel burning apparatus, such as industrial and domestic heating devices of the intermittently operating types, conditions within the combustion chamber of the heating apparatus in connection with a period of inaction are unsuited to full normal'fuel burning op that other dangerous and/or undesirable consequences may occur. Also, such operation involves waste of fuel, and hence a dangerous and uneconomical operation would result.

To correct the disadvantages of previous methods of fuel burning, applicants mechanism includes a valve movement restricting device, which, as shown herein, may be constructed as to comprise essentially the bi-metallic arm and the heating element I05 therefor. The switch I0! is normally placed in a circuit-closed position, and consequently when the control device I6 is actuated to its circuit closing condition the heating element I05 is energized simultaneously with the energization of the electro-magnetic device. The bi-metallic arm 80 and its extension leaf 84 are so shaped and arranged as to normally provide, by means of the resiliency of the material from which they are formed, a cushioned resistance to upward movement of the valve 44, by reason of the bearing of the leaf 84 against the shoulder 92 'of the pin 86. The energization of the heating element I05, however, procures the generation of heat therein which gradually radiates therefrom. and permeates the insulation thereof and reaches the adjacent portion of the to change in shape in accordance with well known principles of the thermostatic art, and the parts are so arranged as to cause the arm 80 to tend to arch and to raise its outer free end upwardly, as .viewed in the flgures, under increasing temperature conditions. Thus, when the control device I6 is actuated to itscircuit closing condition the auxiliary valve "iflvis'immediately opened and causes the creation of valve unseating fluid pressure forces tending to movefthe valve 44 toward its open position, but such motion is immediately resisted by the bi-metal arm 8|! which is in its normal or low arched condition. The jl arm 80, however, being in the form of afcantilever extension and being formed of metal-As somewhat resilient and functions in the manner of a sprin permitting the valve 44 to move aslight distance away from its seat 40' in response to'the fluid pressure forces hereinabove described.

Thus, an initial flow of fuel of. reduced proportion is permitted into the combustionchamber of the device for ignition by means of a pilot flame or any other suitable form of igniter as may be desired. This initial combustion is amply accommodated by the reduced draft and temperature conditions in the combustion chamber at the moment, and provides for heating the combustion chamber and the establishment of a smooth flowing draft through the flue of the device. As the temperature within the combustion chamber rises, due to the intial combustion process, the fuel burning apparatus becomes progressively capable of accommodating increased flow of fuel, and the bi-metallic heating element of the device is so arranged as to provide for a gradual changing of the shape thereof over a predetermined lapse of time in such manner that the restraint of motionof the main valve 44 is gradually released as the generated heat permeates the bi-metallic element, to-permit the valve 44 to be moved in response to fluidprese sure forces thereon to increasingly higher positions and toward the full open position indicated in Fig. 9. Hence, means have been provided for restraining the movement of the valve element of the mechanism during the valve opening process in such manner as. to permit a varying'flow of fuel through the device in accord with the capacity of the fuel burning portion of the apparatus during the starting-up process. viously, the bi-metallic arm 80 may be formed in any desired manner to provide any desired heat responsive action characteristics. The extension piece 84 may similarly be so formed and arranged as to cooperate in the provision of different desired performance characteristicaand the'adjustment screw I may be adjusted at will to vary the performance characteristics under any given circumstances to meet. difl'erent operating conditions. For example, the adjust-" ment screw I00 may bemanipulated to correct the functioning of the device under different out side temperature conditions. For instance, it will be apparent that if the normal temperature of the atmosphere surrounding the valve device in connection with any given installation is higher than the normal temperature of the atmosphere surrounding the valve device in another given instance, it will be necessary to adjust the setting of the adjustment screw I00 accordingly, so that an initial restraining action against movement of the mainvalve 44 will exist immediately upon opening of the auxiliary valve 50 until after a predetermined time has elapsed.

Fig. 9 illustrates the position of the valve and valve movement restraining element whenever the full unrestrained eifect of the valve lifting fluid pressure forcesis exerted upon the valve by reason of the fact thatthebi-metallic arm 80 through the leaf 84, exerts'no force upon the valve in either direction of its movement, and the main valve 44 is thus being supported in the position shown by the fluid pressure forces exerted thereagainst which are caused by move ment of fluid through thedevice. In many instances the movement of the valve 44 to the position shown in Fig. 9 will suflice to provide for sufficient flow of fluid through the mechanism in view of the magnitude of the pressure existing in the line of the fluid source. In other cases, however, and whenever it is desirable to provide a valve device with a minimum pressure drop between the inlet and outlet ports thereof under full open conditions, the operation of the bi- ,metallic arm may be availed of to relieve the fluid stream of the'pressure-loss attendant to the support of the valve member 44 in its full open position, aswhereinabove described. In such case provision is made to enablethe bi-metallic arm 80 to continue to rise upwardly at its outer or free end beyond the position indicated in Fig. 9 to the position indicated in Fig. 10 wherein the arm 80 and the leaf 84 have been moved to a super-elevated position and support the full weight of the valve 44, having raised the valve 44 upwardly and beyond its normal full open position of Fig. 9. Thus, the efiectlve fluid carrying capacity of the device has been increased. Hence, under this condition, no fluid pressure is required to support the valve and to maintain it in open position, and if the ports and chamber portions of the mechanism are provided of ample dimensions to suit any given condition of operation, the device will function with a minimum pressure loss between the inlet and outletports thereof.

In connection with the valve closing operation of the device, the main valve 44 is adapted to be actuated toward its valve seatedposition in response to actuation of the auxiliary valve 50, in a ,novel and advantageous manner. Closing-of the auxiliary outlet port 49 by the auxiliary valve 50, as by pivotal action of the lever 52 in response to release thereof when the electro-magnetic device is de-energized upon actuation of the control device l6 to its inoperative position, terminates the previous flow of fluid from the valve chamber 48 into the outlet port 34 and causes a sudden building up of static fluid pressure within the valve chamber and above the main valve 44 which tends to move the valve 44 downwardly toward its seated position. This downwardly directed force upon the valve 44 is temporarily resisted, however, by the arm 80, but because of the resiliency of the spring 96 the valve 44 is motivated to some extent relative to the leaf 84, and a partial reduction of fluid flow through the device takes place immediately and simultaneously with the closing of the auxiliary valve 50. However, the heating element I05 is also de-energized at the time of the de-ene'rgization of the electro-magnet and hence the bimetallic arm begins to cool and tends to graduaewaae boss M. and the threaded portion of the pins 86 ally assume its normal inoperative shape. As this cooling progresses the static fluid pressure above the valve M continues to urge the valve (Fig. 11) toward its seated position and in time this force is joined in its effect by a similarly directed force resulting from the creation of a suction adjacent the central lower surface of the valve it which is due to the creation of a vortex type of fluid flow through the opening of the partition to and toward the outlet port of the device. Also, as the valve ll-t approaches its seated position and thus cuts ofi the volume of fluid flow through the device, the momentum of the fluid in the fuel discharge line provides an additional downwardly directed force upon the valve id in the form of an increased suction operating adjacent the underneath surface thereof.

Consequently, as the valve i l approaches its seated position in response to relinquishment of upwardly directed supporting forces oi the bimetallic arm (it, it comes successively into the range of additional and increasingly greater downwardly directed forces which increasingly overpower the resistance of the coil spring as and ultimately cause the valve M to be seated with a, snap-like action (Fig. 12) despite the fact that the arm as has not yet assumed its normal inactive attitude. Hence, means have been provided for restrainingthe valve closing action of the device in such manner as to prevent the sudden cessation of fluid flow therethrough, such as wouldbe undesirable in many types of weather conditions to arbitrarily limit the heating degree of the apparatus to the end that a more steady and low-flame operation may be obtained as distinguished from a more intermittent and high-flame operation. In such case the switch id'i of the heating element circuit may be left open, and the bi-metallic arm til will therefore constantly tend to maintain its normal inactive shape and will operate constantly to restrict movement of the valve id in response to fluid pressure forces directed thereagainst application." For example, in connection with heating apparatus of the fluid fuel lntermit-' tently operating types, the sudden cutting ofi of the flow of fuel into the combustion chamber thereof will produce popping noises and concussions in the fuel lineinaccord with the principles of the well known'hammer action of fluids under suppressed momentum conditions.

It will be apparent that the relation and inter-,

action of the various valve opening and closing forces hereinabove described may bevaried to suit difierent operating conditions and waive any performance characteristic that may be desired by varying the relative arrangements and proportioning of the actuating elements thereof, and by varying the relative adjustment of the elements of the device as provided for.

Fig. 6 illustrates another form oi connection between the leaf M and the valve pin 86. wherein an adjustable abutting connection therebetween is provided. In this form of construction the pin to is threaded through a boss as carried by the leaf 8% for vertical adjustment relative to the leaf M by manual turning of the pin dd as by means of a head t'l thereon and abuts, at its lower end the upper surface of the yalve M. Hence, no resiliency is provided in the connection between the leaf 84 and the pin 8t, and during the valve closing movements or the mechanism the arm to has no restraining effect upon the valve til, the valve 44 beins free from the pin 86 for movement downwardly away therefrom. In some types of applications this form oi construction will operate quite satisfactorily, and may even be preferred, according to the type of performance characteristics desired. The boss 83 is preferably provided during the course of its construction and after being threaded, with a slot 85 extending substantially therethrough. The boss is then upset, as by pressing upon its opposite ends. There is thus provided a selflocking threaded connection between the whenever the auxiliary valve is opened. Consequently, wherever the control device it operates to cause the auxiliary valve fill to open, the main valve t l will be opened to only some slight degree in response to fluid pressure forces thereagainst, and the bi-metallic arm til will continue throughout the burning operation to maintain the valve in its partially open condition. The adjustment screw Hid may be manipulated to give any desired performance characteristics under such operating conditions.

It will be apparent that by reason of my novel construction, during operating conditions a constant flow of fluid will passthrough the valve chambers of the device about the valve movement restrictive elements thereof in such'manner as to efiectivelyventilate the valve chambers and adjacent portions of the valve structure to the end that no substantial amount of heat is permitted to be stored up in the structural elements thereof, as might otherwise occur from transfer of the heat generated by the heating element ldii to adjacent portions of the valve structure. Hence, immediately upon disruption of the heating element circuit in response to valve closing adjustment of the control element it, the bimetallic arm dll will commence to cool and the valveclosing operation will therefore not be unduly delayed, as would otherwise occur if heat had been stored in the adjacent valve structure during the valve open cycle of the operation. i

It will be apparent that application of the principles of the present invention are not to be limited to the use of a valve movement restraining element of the specific torm illustrated and described hereinabove, and that any other suitable form of heat responsive unit may be employed in lieu of the bowed lei-metal arm 80. For example, a monometal heat responsive unit of the types employed in the thermostat art, or any other unit which will have a tendency to change in shape main valve dd relative to the valve seat member till and the resultant varying volume of fluid flow through the device during a complete hypothetical cycle of valve opening and closing operation. The solid line curve of Fig. 2 illustrates the valve movement and varying rate of fluid flow in the case of the form of valve construction illustrated -ln Figs. 3, 5, and 8 to 12 inclusive, wherein the arm 80 is connected through means of the leaf 84 to the valve 44 in'such manner as to restrain both the opening and closing movements of the valve 44. The broken line curve of Fig. 2 illustrates graphically the difierence between the movements of the valve member 44 and the resultant rates of fluid flow when the valve is associated with therestraining element in the manner illustrated in Fig. 6 and the results obtained bythe form of construction shown in Figs. 3 and 5 which are illustrated by the solid line curve. .The point 200 indicates the rate of fluid flow immediately attained upon actuation of the auxiliary valve 50 to,its open position before the heat generated by tlie element I05 penetrates the arm 80. The set screw I00 may be adjusted, if desired, to provide an initial tension between the arm 80 and the valve 44 tending to urge the valve downwardly against its seat to such degree that the alteration of fluid pressure forces upon the valve 44 upon the opening of the auxiliary valve Y 50 fails to effect a change of fluid forces sufficient to overcome the resistance of the arm 80 to upward movementof the'valve 44. In such case, the point 200 on the curve will indicate the rate of fluid flow through the auxiliary port 49 and the gap 46 around the main valve of the device. However, if the set screw I00 is adjusted to a position .whereby' there is' a relatively reduced initial tension-between the arm 80 and the valve 44 tending to resistupward movement of the valve, the point 200 on the curve will indicate an increased initial rate of fluid flow comprising a combination of the flow through the auxiliary,

port 49; and a restricted flow between the valve 44 and the valve seat element 40 which results from a slight upward movement of the valve 44 in response to the creation of a fluid pressure force differential tending to raise the valve 44 which overcomes the tension of the arm 80 im: mediately upon opening of the auxiliary valve 50.

The portion of'the curve between points 200 and 202 indicates the time lapse between the initial opening of the auxiliary valve 50 and the beginning of the relinquishment of the valve restraining wtion of the arm 80 as a result of the the resistance of the coil spring 96 and cause the valve 44 to complete the terminal portion of its closing operation with a snap-like and positive seating movement (Fig. 12), as indicated by the curve below the point 2l0.

The broken line curve portions of Fig. 2 illustrate graphically the deviations of the movements of the valve .44 and of the resultant rates of fluid flow through the device from the performance of the valve as illustrated by the solid' line curve that occur in connection with the use of the form of construction illustrated in Fig. 6. In this form of.construction the valve restrictive element 80 is associated with-the valve member 40 in abutting relation only, and therefore is only 'capable of restricting the opening movements of the valve 44. Consequently, as illustrated by the portion of the broken line curve between points 204 and 212, the valve 44 moves upwardly only as far as the open position indicated by the point 204, (Fig.- 9), and is not carried further upwardly by any lifting action of the arm 80, as in the case of the first mentioned form of construction.

Also, upon closing of the auxiliary valve 50, as at point 212 on the curve, thefluid pressure forces of the device act freely upon the valve 44 without restraint by the restrictive elements of the device and produce an immediately complete closing of the valve, thus cutting off all fluid flow therethrough. As explained hereinabove each of these forms of construction may have advantageous applications, depending upon the type of valve movement characteristics desired in any given i may be made therein without departing from the spirit of the invention or from the scope of the appended claims.

penetration of heat thereto from the heating ele- 4 arm 00 yields upwardly to the fluid pressure force.

differential hereinabove described, which tends to lift the valve ,44 to the position shown in Fig. 9. The portion of the curve between points 204 to 206v indicates the further upward movement of the valve-and the increased rate of fluid flow through the device in response to the positive lifting movement of the arm 80 which takes effect after the fluid pressure forces of the device have lifted the valve 44 to the utmost of their ability, and the portion of the curve between points 206 and 208 indicates the position of the valve 44 and the rate of fluid flow through the device when the valve is in the position shown in Fig. 10. The portion of the curve between points 2M! and 210 indicates the movements of the valve 44 and valve closing forces which ultimately overcome I claim:

1. A device for restraining movement of a valve relative to its seat, including a bi-metallic cantilever arm, a second arm mounted upon the free end of said bi-metallic arm and having a portion extending in spaced relation therefrom, means for adjusting the position of the extending end portion of said second arm relative to said bi-meta-llic arm, resilient-means for connecting the outer extending portion of said second arm and said valve and controlled means for applying heat to said bi-metallic arm.

2. A devicevlfor restraining movement of a valve relative to its seat, including an element adapted to change in shape under changing temperature conditions, a second arm mounted'upon the free end of said shape changing element and having a portion extending in spaced relation therefrom, means for adjusting the position of the extending end portion of said second arm relative to said shape changing element, resilient means for connecting the outer extending portion of said second arni and said valve and controlled means for applying heat to said shape changing element.

3. In a fluid control valve mechanism, inlet and outlet chambers adjacent one another and divided by a partition member defining a valve seat portion therebetween, a static fluid pressure chamber in open communication at one end with said inlet chamber and provided with an auxiliary conduit in open communication with said outlet chamber, a relatively light weight primary valve disposed in freely movable relation in said pressure chamber, an auxiliary valve member adapted to close said auxiliary conduit between said pressure chamber and said outlet chamber, and means for moving said auxiliary valve to and from closed positions relative to said conduit to vary the static fluid pressure within said pressure chamber, whereby said primary valve is actuated by combined dynamic and static fluid pressure differentials upon opposite sides thereof relative said valve seat portion, and means resiliently resisting movement of said primary valve for delaying the operating movements thereof.

i. In a fluid control valve mechanism, inlet and outlet chambers; adjacent one another and divided by a partition member defining a valve seat portion therebetween, a static fluid pressure chamber in open communication at one end with said inlet chamber and provided with an auxiliary conduit in open communication with said outlet chamber, a relatively light weight primary valve disposed in freely movable relation in said pressure chamber, an auxiliary valve member adapted to close said auxiliary conduit between said pressure chamber and said outlet chamber, and means for moving said auxiliary valve to and from closed positions relative to said conduit to vary the static fluid pressure within said pressure chamber, whereby said primary valve is.

actuated by combined dynamic and static fluid pressure differentials upon opposite sides thereof relative said valve seat portion, and means resiliently resisting movement of said primary valve away from said valve seat portion for delaying the valve opening operation thereof.

5. In a fluid control valve mechanism, inlet and outlet chambers adjacent one another and divided by a partition member defining a valve seat portion therebetween, a static fluid pressure chamber in open communication at one end with said inlet chamber and provided with an auxiliary conduit in open communication with said outlet; chamber, a relatively light weight primary valve disposed in freely movable relation in said pressure chamber, an auxiliary ,valve member adapted to close said auxiliary conduit between said pressure chamber and said outlet chamber, and means for moving said auxiliary valve to and from closed positions relative to said conduit to. vary the static fluid pressure within said pressure chamber, whereby said primary valve is actuated by combined dynamic and static fluid pressure differentials upon opposite sides thereof relative said valve seat portion, and

means for temporarily restraining movements of said primary valve throughout a predetermined time period.

6. In a fluid control valve mechanism, inlet and outletchambers adjacent one another and divided by a partition member defining a valve seat portion therebetween, a static fluid pressure chamber in open communication at one end with said inlet chamber and provided with an auxiliary conduit in open communication with said outlet chamber, a relatively light weight primary valve disposed in freely movable relation in said pressure chamber, an auxiliary valve member adapted to close said auxiliary conduit between said pressure chamber and said outlet chamber, and means for moving said auxiliary valve to and from closed positions relative to said conduit to vary the static fluid pressure within said pressure chamber, whereby said primary valve is actuated by combined dynamic and static fluid pressure diflerentials upon opposite sides auxiliary conduit in open communication with said outlet chamber, a relatively light weight primary valve disposed in freely movable relation in said pressure chamber, an auxiliary valve member adapted to close said auxiliary conduit between said pressure chamber and said outlet chamber, and means for moving said auxiliary valve to and from closed positions relative to said conduit to vary the static fluid pressure within said pressure chamber, whereby said primary valve is actuated by combined dynamic and static fluid pressure diiierentials upon opposite sides thereof relative said valve seat portion, and means for restraining movements of saidprimary valve in varying degrees in accord with predetermined time lapses including a heat responsive element and a heat supply means associated therewith and means for controlling the supply of heat to said element in such manner as to vary the restraining effect of said element according to predetermined conditions.

8. In a fluid pressure control-valve mechanism,

inlet and outlet chambers separated by means defining a valve seat, a pressure chamber in open communication with said inlet chamber, a control element normally held in a closed position relative to said valve seat by the pressures existing insaid pressure chamber and having intermediate and open positions, means operated in response to a change in a predetermined atmospheric condition for communicating said pressure chamber with said outlet chamber to thereby release the pressure on said control element to cause movement thereof to its intermediate position, whereby fluid pressure flows from said inlet chamber to said outlet chamber urging said control element toward its open position, and means controlled by said condition responsive means for subsequently permitting movement of said control element to said open position;

9. In a fluid pressure control valve mechanism, inlet and outlet chambers separated bymeans defining a valve seat, a pressure chamber in open communication with said inlet chamber, an auxiliary chamber joining said pressure chamber and said outlet chamber, an auxiliary valve closing said pressure chamber from said outlet chamber, a control element normally held in a closed position relative to said valve seat by the pressures existing in said pressure chamber and having intermediate and open positions, means operated in response to a predetermined atmospheric condition for actuating said auxiliary valve to thereby release the pressure onisaid control element to cause movement thereof to its intermediate position, whereby fluid pressure flows from said inlet chamber to said outlet chamberurging said control element to its open position, and means her, and interrupting means including a bimetallic element operative to stop valve movement for a time period while said valve is moving from said first to said second position at a position intermediate said first and second positions, and means responsive to a predetermined atmospheric condition for increasing thelpressures in said pressure chamber whereby said pressures act upon said valve against the action of said interrupting means when said valve is moving from said second to said first position in the course of its normal operation.

11. In combination, a valve comprising a floating disc adapted to be moved between first and second positions by the pressure of the. fluid controlled by said valve, means for controlling said fluid pressure to actuate said disc, interrupting means comprising a bi-metal element providing a stop for said disc to stop movement thereof at 9. position intermediate said first and second posecond positions by the pressure of the fluid con-' trolled by said valve, means for controlling said fluid pressure to actuate said disc, and interrupting means including a timing device operative to stop movement of said disc at a position intermediate said first and second positions for a predetermined time while moving from said first to said second position, said interrupting means being ineflective to stop movement of said disc while the latter is moving from said second position to said first position in the course of its normal operation.

13. In combination, a valve comprising a floating disc adapted to be moved between first and second positions by the pressure of the fluid controlled by said valve, means for controlling said fluid pressure to actuate said disc, interrupting means including a timing device operative to stop movement of said disc at a position intermediate said first and second positions for a predetermined time'while moving from said first to said second position, said interrupting means being ineifective to stop movement of said disc while the latter is moving from saidsecond position to said first position in the course of its normal operation, and means responsive to a predetermined conditioning for controlling said interrupting means.

14. In combination, a valve comprising a floating disc adapted to be moved between first and second positions by the pressure of the fluid controlled by said valve, means for controlling said fluid pressure to actuate said disc, means for actuating saidcontrolling means, and interrupting means including a timing device operative to stop movement of said disc for a predetermined time at a position intermediate said first and second positions while said disc is moving from said first to said second position, said interrupting means being ineffective to stop movement of said disc when the latter is moving from said second position to said first position.

15. In combination, a valve comprising a float-- ing disc adapted to be moved between first and second positions by the pressure of the fluid controlled by said valve, means for controlling said fluid pressure to actuate said disc, means for actuating said controlling means, interrupting means including a timing device operative to stop movement of said disc for a predetermined time at a position intermediate said first and second positions while said disc is moving from said first to said second position, said interrupting means being ine'fl'ective to stop movement of said disc when the latter is moving from said second position to said first position, and means responsive to an atmospheric condition for controlling said interrupting means.

NICO BORRESEN.' 

